Liquid flow control system



March 22, 1938. E. J. CRANE LIQUID FLOW CONTROL SYSTEM Filed OGV. 12,

mim/R5 `55 draulic motor;

Patented Mar. 22, 1938 PATENT OFFICE e LIQUID FLOW CONTROL `SYSTEM Edward J." Crane, Oak Park, Ill., assignor toV Western Electric Company, IncorporatedNew York, N. Y., a corporation of New York Application October 12, 1932, Serial No. 637,439

2 claims.` (o1. sli-52) i This invention relates to liquid flow control systems, and moreparticularlyto a system for controlling the flow of liquid under pressure, and is a part continuation of my copending appli- 5 cation, SeerialNo. 468,191, filed July 15, 1930. The primary object` of this invention `is to provide an improved hydraulic medium ow controlA systemfor operatinghydraulic motors.

In accordance with one-embodiment of this 10 invention as applied'to a reciprocatory type of hydraulic motor, there is provided a liquid flow controlsystem connected to the hydraulic cylinder of the motor, and, a constant delivery liquid pump.' The control system consists of a by-pass `15 around the pump which includesV a `manually operable throttle valve'which has its discharge side connected to the inlet side :of the pump. Also included in the by-pass is a pressure regulating valve with a substantially balanced plunger provided with liquid throttling passages and -3 means for applying a constant force thereto, the

inletside oi the pressure regulating valve being i e connected to the cylinder as well as to the pump and its, discharge sideconnected to the inlet side of the throttle l, valve. The connection between the valves is also connected to a port in the pressure regulating valve below the plunger thereof. 'With this arrangement thepressure between the valves is proportional to theconstant force apvalveplunger. A constant pressure is, therefore, maintained on the inlet side of the throttle valve and this insures a constant rate of flow through the latterand `hence a constant rate of ow 3,. through `the by-pass as a whole, the rate'oi flow being determined by adjusting the manuallyY The maintenance of a operable throttle valve. constant, manually controllable flow through the by-pass combined with the use of a constant de- 40 livery pump makes it ,possible to operate the reciprocatory motor at any predetermined constant rate of speed. i

Inariother embodiment of the invention the pressure liquid may be caused to. be by-passed 45 at a predetermined variablerate of flow, depending upon the resistance encountered by the reciprocatory motor. e Y

Other objects and advantages of this invention accompanying drawing, wherein Fig.` 1 'is a diagrammatic view, partly in section; of 'a liquid flow control system embodying the features of this invention applied to a hyplying means `acting on the pressure regulatingV Fig. 2 is an alternative embodiment of theV means shown in Fig. 1 for maintaining a substantially constant force on the pressure regulating valve plunger, and e Fig. 3 is an alternative embodiment oithe in- 5 vention, shown fragmentarily, for causing the pressure medium .tobe by-passed at a predetermined variable rate of ow depending upon the resistance encountered by the reciprocatory mot0?. v 10 Referring now to the drawing, and 'particularly to Fig. 1, there is illustrated fragmentarily a hydraulically actuated ram` I Il, which may be connected to a material working apparatus;l forinstance, a machine tool feed (not shown), the 15 ram beingintegral at its upper end with a piston I I reciprocable 'within a hydraulic motor cylinder I2. The `piston II is actuated by pressure liquid; for instance, oil, supplied'to the cyl-` inder I2 at opposite ends of the piston I I through let port `of the pump I1 is connected by a'pipe Vliquid regulating valve 26, to be presently described. The inlet port of thepumpli and also the valve I3 are connected to a liquid supply reservoir 21 by pipes 28 `and '29,` respectively,-

i Since the details .ofthe pump I'I and the valve 7 I9 are not necessary to a complete understanding of this invention a detailed disclosureV vand description thereof will not be given herein.

Referring to Fig. 1, the pressure liquid regulating valve 26 comprises a casing 3| provided 45 with a longitudinally extending bore 32 within which is reciprocably mounted a plunger 33 having a reduced intermediate portion 34 providing substantially equal annular pressure surfaces 35 and 36. Formed peripherally in the plunger 33 50 beginning at the surface 36 are a plurality `of equally spaced tapered V-shaped liquid throttling passages o r slots 31 through which the pressure e liquid is throttled froma chamber 38 of the valve 26 formed between the surfacesA 35 and 36 to an 55 outlet port 46 of the valve. The upper end of the plunger 33 extends through the casing 3l and is provided with an enlargement or weight 4I, the purpose of which will be made apparent hereinafter. Between the lower end surface of the plunger 33 and the opposed inner surface of the valve casing 3| is a chamber 42. The outlet port 40 of the valve 26 is connected by a pipe 43 to a manually operable valve 44 of a known type, such as an ordinary needle valve, and the outlet side of the latter is connected to the reservoir 21 by a pipe 45. Intermediate the outlet port 40 of the valve 26 and the throttle valve 44 the pipe 43 is connected to a pipe 41 which is connected to a port 48 communicating with the chamber 42 of the valve 26.

The operation of the herein described liquid flow control system, assuming a constant delivery of pressure liquid by the pump I1, and that all slippage of the pump and leakage of the liquid pastthe piston II of the cylinder I2 or other liquid leaks in the system have been suitably compensated for is as follows: It is to be understood that in the normal condition of the liquid flow control system it is lled with liquid. The pressure liquid in the position of the valve I9 as shown in Fig. 1 will be directed from the pump I1 through the pipe I8, valve I9, and the pipe 20 into the upper end of the cylinder I2 and simultaneously through the pipes I8 and 24 into the chamber 38 of the pressure regulating valve 26. The liquid directed into the valve 26 exerts a substantially balanced pressure upon the plunger 33 thereof, as hereinbefore described, and is throttled through the V-shaped slots 31 of the plunger and passes through the outlet port 40, the pipe 43 and the throttle valve 44 to the reservoir 21. By means of the pipe 41 the pressure of the liquid between the valves 26 and 44 is transmitted into the chamber 42 and against the bottom of the plunger 33. v

It is evident that with this arrangement the pressure of the liquid between the outlet port 40 of the valve 26 and the throttle valve 44 is proportional to the weight on the valve plunger 33; that is, for any given weight the pressure at this point will remain constant, regardless of the pressure in the pipe 24, which is substantially equal to that in the cylinder I 2 and by means of which the working resistance is overcome. The flow through the throttle valve 44 will therefore be constant forv any given setting thereof, the valve 44 being set according to the desired speed of operation of the apparatus. Due to the pressure liquid being by-passed at constant rate it will be delivered at a constant rate tothe cylinder I2 and therefore the ram I will move downwardly at a constant rate of speed, regardless of variations in the working resistance it encounters. For example, if during the downward movement of the ram IIJ an increased resistance is encountered, an increase in the pressure of the liquid will occur in the cylinder I2 and a corresponding increase in pressure will be immediately transmitted to the pressure regulating valve 26 by means of the pipe 20, the valve I9 and the pipes I8 and 24, and will cause a momentary increase in the ow of the liquid through the V-shaped slots31 of the plunger 33 and the throttle valve 44. The increased flow through the throttle valve 44 will raise the pressure in the pipes 43 and 41 between the valves 26 and 44, which increase in pressure is immediately transmitted into the chamber 42 and against the bottom of the plunger 33, causing the latter to move upwardly slightly, thus partially closing the V-shaped slots 31 of the plunger to the ow of the pressure liquid through the valve 26, and thus again restricting the ow through the pipe 43 and throttling valve 44 until the pressure in the pipe 43 is brought back to its original value, where the pressure exerted against the bottom of the plunger 33 again just balances the weight 4I. In the case of momentarily reduced pressure of the liquid in the cylinder I2 a similar but reverse action occurs in the system to that hereinbefore described.

In another position of the valve I8 after the ram I0 has been lowered, the pressure liquid may be directed from the pump I1 through the pipe I 8, the valve I8, the pipe 2I, into the lower end of the cylinder I2 to return the ram I U, and simultaneously therewith the liquid is directed into the valve 26. A similar action to that previously described in connection with the downward movement of the ram I0 takes place In the valve 26 to return the ram I0 at a constant speed, which in the case of some machine tools is desirable. During the downward movement of the ram I Il the liquid below the piston II escapes through the pipe 2I, the valve I9, and to the reservoir 21 by means of the pipe 28, while during an upward movement thereof the liquid above the piston escapes 'through the pipe 20, the valve I9 and the pipe 29.

As the purpose of the weight 4I on the valve plunger 33 is merely to maintain a constant force acting against the plunger any suitable means for securing the same result may be employed. In Fig. 2 an alternative means is disclosed comprising a compression spring 52 mounted in the valve casing 3I and acting against the upper end of the plunger 33 with a substantially constant force within the limits of the motion of the plunger 33. The compression of the spring 52 may be regulated by means of an adjustable seat 53 at its upper end. It will be evident that a constant pressure liquid acting against the top of the plunger 33 would also serve the same purpose as the weight 4I or spring 52. By varying the weight 4I or other force acting against the plunger 33 it is possible to cause the pressure liquid to be by-passed at a predetermined variable rate of flow, depending upon the pressure in the cylinder I2. This principle can be used to make the rate of iiow vary in any arbitrary way, depending upon the resistance encountered by the ram I0 or other part being moved. For example, in the case oi the spring 52 (Fig. 2) the rate at which the liquid is by-passed will increase as the pressure in the cylinder I 2 increases.

In the embodiment illustrated in Fig. 3 the f upper surface of the weight 4I is connected as indicated at 55 to one arm of a bell crank lever 56 by a exible member 51, the lever being pivoted at B to astationary bracket 58. Another arm of the lever 56 is in the form of a suitably shaped cam 60 having attached to the upper end of its ca m face as indicated at 6I a exible member 62 to the lower end of which is attached a weight 63. When the weight 4I moves upwardly due to an increase of pressure in the cylinder I2 an increased leverage on theA bell crank lever 56 occurs due to the weight 63 moving farther away from the pivot 58 and thus lowering the pressure required in the chamber 42 in order to balance the weights 4I and 63 and associated leverage system. This reduction in pressure in the chamber 42, conduits 41 and 43 will result in a reducu tion of therate at which the pressure medium is discharged through the throttle valve M. In the case of reduced pressurev in the cylinder l2 a lsimilar but reverse action Voccurs in the system to that just described. It will be obvious that increased hydraulic slippage, liquid leaks and the reduced pump motor speed normally occurring at increased pressures can be readily compensated for by-proper proportioning of the parts.

It is believed that the advantages of the present invention will be clearly apparent from the above detailed description. By the use of the ini vention a hydraulically operated motor may be i operated at predetermined rates `of speed, re-

gardless of the fact that the resistance it encounters may vary within wide limits. Y

The liquid flow control system embodying the features of this invention has been disclosed as `applied to a reciprocatory type of hydraulic motor for use inconnection with machine tools,

`but it willbe obvious that it may also `be applied to hydraulic motors of known construction dei i. (signed to deliverv rotary motion, and also to any hydraulic mechanism wherev it is desired to bymay notbe of sufcient magnitude to require correction. Obviously such variables should be coni with sufcient accuracy for the particular Workv "being done, but for some purposes no special control. of these'variablesmay be needed. In order to simplify the disclosure the drawing has been pass a part of the liquidat a constant rate.

It is to be understood that in the specification and claims the expressions substantially coni stant flow and substantially constant pressure do not take into "account controllable variables,`

such as `the viscosity of the oil, since these may or trolled so as to enable the machine to operate l. made schematic and since accessory controls of stant rate, motor means actuated by said pressure' medium, a conduit for by-passing a' portion of said pressure medium from said motor means, a by-pass valve in said conduit, and a pressure equalizing valve arranged in said conduit between said motor means and said by-pass valve, said pressure equalizing valve being operably responsive to variations in pressure applied to said motor means for maintaining constant the pressure applied to said by-pass valve, said by-pass valve being ladjustable to vary the speed of the motor means.

Z; A hydraulic flow control system comprising a source of pressure medium delivering at a constant rate, motor means actuated by said pressure mediuma conduit for py-passing a portion of said pressure medium from said motor means, a

throttling valve in said conduit adjustable to have an orifice of fixed size, and means in said conduit preceding said throttling valve in the direction of flow of said pressure medium for maintaining. a constant pressure of the pressure medium on said throttling valve orice, whereby for a given adjustment of said throttling valve the speed' of said motor means is maintained constant when the load thereon varies.

EDWARD J. CRANE. 

